Rotor system having alternating length rotor blades for reducing blade-vortex interaction (BVI) noise

ABSTRACT

A rotor system (4) having odd and even blade assemblies (O b , E b ) mounting to and rotating with a rotor hub assembly (6) wherein the odd blade assemblies (O b ) define a radial length R O , and the even blade assemblies (E b ) define a radial length R E  and wherein the radial length R E  is between about 70% to about 95% of the radial length R O . Other embodiments of the invention are directed to a Variable Diameter Rotor system (4) which may be configured for operating in various operating modes for optimizing aerodynamic and acoustic performance. The Variable Diameter Rotor system (4) includes odd and even blade assemblies (O b , E b ) having inboard and outboard blade sections (10, 12) wherein the outboard blade sections (12) telescopically mount to the inboard blade sections (10). The outboard blade sections (12) are positioned with respect to the inboard blade sections (10 such that the radial length R E  of the even blade assemblies (E b ) is equal to the radial length R O  of the odd blade assemblies (O b ) in a first operating mode, and such that the radial length R E  is between about 70% to about 95% of the length R O  in a second operating mode.

The invention described herein was made in the performance of work under NASA Contract No. NAS 1-20097 and is subject to the provisions of Section 305 of the National Aeronautics and Space Act of 1958 (72 Star. 435; 42 U.S.C. 2457).

TECHNICAL FIELD

The present invention is directed to means for reducing the noise radiated from the rotor blades of rotorcraft, and, more particularly, to means for reducing Blade-Vortex Interaction (BVI) noise radiated from such rotor blades when operating in flight modes which produce high levels of BVI noise.

BACKGROUND OF THE INVENTION

One concern of rotorcraft designers is to reduce, to the extent practicable, the noise radiating from the rotor blades during flight operations. In particular, landing approaches which are characterized by a low speed, descending flight profile produce significant noise levels due to acoustic emissions known as Blade-Vortex Interaction (BVI). Insofar as such flight profile typically occurs at low altitude and over populated areas, BVI noise presents a primary technical issue which must be resolved to obtain community acceptance, and, more importantly, certification of newly-developed rotorcraft.

During typical rotorcraft flight operations, the rotor blades create a high velocity, low pressure field over the upper aerodynamic surface thereof and a low velocity, high pressure field over the lower aerodynamic surface. The pressure differential generates the necessary lift forces for flight operations but, additionally, effects the generation of vortices at the tips of the rotor blades. More specifically, the pressure differential engenders airflow circulation from the high pressure field to s the low pressure field to create a tip vortex. A tip vortex is shed from one rotor blade and impinges/interacts with a subsequent rotor blade as it rotates through the vortex field. The interaction of a tip vortex with a rotor blade induces impulsive airloading which creates an acoustic pressure wave that is the source of BVI noise.

BVI noise is generally not a concern in ascending or cruise flight modes inasmuch as the rotor disk, i.e., the plane defined by the rotor blades, moves away from the vortex wake. Consequently, the vortices are distally spaced from the rotor and do not significantly interact therewith. BV Interactions are most prevalent, however, during descent modes of operation, insofar as the downward velocity of the rotorcraft causes the rotor to fly into its wake thus interacting with multiple vortices.

The trajectory and core strength of vortices are difficult to predict; however, it may be generally stated that the vortices move downward in a spiral pattern as a function of the speed and flight attitude of the rotorcraft, the boundary conditions imposed by the fuselage, the turbulence of the atmosphere, and other factors such as the lift-time history of each rotor blade. Generally, BV Interactions which occur in the first quadrant of the rotor disk (0 degrees being positionally aft of the rotor shaft axis and along the longitudinal axis of the rotorcraft) generate strong BVI impulses due to the combined rotational velocity of the rotor blades and the forward flight velocity of the rotorcraft. Furthermore, the probability for strong interactions is intensified due to the high concentration and strength of vortices in this quadrant.

Another factor which influences the strength of the BV Interactions includes the orientation of the rotating vortex with respect to the impinging rotor blade. The orientation of the vortex is defined by the angle of intersection between the leading edge of the rotor blade and the centerline of the vortex, i.e., vortex core. When the orientation is substantially parallel with respect to the rotor blade leading edge, the circulatory flow of the vortex affects a large portion of the blade length, and, consequently, excites large impulsive pressure waves. Orientations which are substantially perpendicular or oblique to the leading edge produce relatively benign interactions by limiting the blade spanwise extent that is exposed to the circulatory flow.

Yet another factor which determines the strength of BVI encounters is the spatial separation between the rotating vortex and a passing/intersecting rotor blade. The spatial separation may be more accurately defined as the distance from the vortex core to a point on the leading edge of the rotor blade. Insofar as the airflow velocity at a point in the vortex field is a function of 1R, wherein R is the distance from the vortex core, it will be apparent that the airflow velocity, in theory, becomes infinite (∞) as R approaches zero (0) and diminishes at a precipitous rate as the distance R increases. Accordingly, when the spatial separation is small, e.g., less than the thickness of the rotor blade, the rotating vortex field will significantly impact the circulation about the rotor blade thereby producing large BVI impulses. Conversely, when the separation is larger, e.g., 5X the thickness of the rotor blade, the BVI impulse is substantially reduced due to the precipitous decline of vortex field velocity at the point of rotor blade intersection.

The rotorcraft designer, therefore, attempts, to the extent practicable taking into account, inter alia, weight, cost, performance, and system complexity, to incorporate elements into the rotor assembly that mitigate the BVI noise radiated therefrom. There are several different design options to mitigate BVI radiated noise. These approaches may be grouped into three broad categories, namely, passive systems, deployable passive systems and active systems.

Passive systems attempt to reduce BVI noise by favorably altering rotor blade geometry or rotor operating parameters. Examples of passive systems include selective tip shaping to diffuse or weaken the vortex. One design option involves a forward swept tip wherein the vortex is generated inboard of the tip, such inboard generated vortex being more diffuse, i.e., reduced in strength, than the tip vortex generated by a conventional rectangular tip. Another design configuration is a sub-wing tip wherein a sub-wing is attached to the rotor blade at the tip thereof to produce two weak, corotating vortices that mix downstream and diffuse due to viscous effects. Yet another design approach involves reducing tip speed, below about 675 ft/sec (206 m/sec), or increasing the number of blades to reduce blade loading, and, consequently, the strength of the tip vortex. These design options provide marginal improvement in mitigating BVI noise, e.g., on the order of about 2 to 5 dBa reduction and, furthermore, often degrade the overall operating efficiency of the rotor system. Furthermore, such design options may be difficult and/or costly to implement.

Deployable passive systems alter the rotor blade geometry in flight by deploying a noise reduction device during modes of operation which produce high levels of BVI noise. Examples of deployable passive systems include half-plow vortex generators which are disposed along the upper or lower surface of a rotor blade and are deployable when the rotorcraft is in a descending flight profile. Similar to the sub-wing tip discussed above, the half-plow vortex generators produce two or more vortices of reduced strength in an attempt to disrupt the formation of a single, more potent, tip vortex. While such vortex generation/deployable devices are generally effective in reducing BVI noise, performance penalties and/or mechanical complexities are impediments to the widespread acceptance of deployable passive systems.

Active systems effect noise control by continuously modifying the pitch or angle of attack of a rotor blade azimuthally about the rotational axis. This may be accomplished via selective control inputs by pitch control actuators or through blade mounted control surfaces which receive control inputs from a closed- or open-loop feedback control system. More specifically, the control system senses vibration/noise via a plurality of accelerometers/microphones and provides higher order control inputs to the control actuators/control surface to pitch the rotor blade at selected higher harmonic frequencies. The higher harmonic blade excursions effect vibration/noise reduction by influencing the trajectory and/or strength of the interfering vortex, and/or producing pressure waves that directly cancel the BVI pressure impulse. One example of an active system includes oscillating flaps disposed along the trailing edge of a rotor blade to provide a means of actively controlling the angle of attack of the rotor blade. Another example involves channeling air to the tip of a rotor blade and expelling such air to disrupt the formation of the tip vortex. Active systems are, perhaps, the most effective in mitigating the BVI noise when compared to passive and deployable passive systems, however, active systems are the most disadvantageous in terms of incurred weight penalties, complexity, reliability and related fail-safe issues.

A need, therefore, exists to provide a means to significantly reduce the BVI noise radiated from rotor systems which does not significantly degrade the operating efficiency thereof, e.g., lift capacity or power requirements, and does not significantly increase the weight, or mechanical complexity of the rotor system.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a rotor system having rotor blade assemblies of alternating length for reducing Blade-Vortex Interaction (BVI) noise.

It is another object of the present invention to provide a Variable Diameter Rotor (VDR) system for reducing BVI noise which VDR system includes telescoping rotor blade assemblies and a positioning means for controlling the length of the rotor blade assemblies such that the rotor blade assemblies are fully-extended in a first operating mode for optimal aerodynamic performance, and alternately vary in blade length in a s second operating mode for optimal acoustic performance, i.e., BVI noise reduction.

It is yet another object of the present invention to provide a VDR system in combination with a tilt rotor aircraft for reducing BVI noise which VDR system includes telescoping rotor blade assemblies and a positioning means for controlling the length of the rotor blade assemblies such that the rotor blade assemblies are extended in a first operating mode for optimal hover performance, alternately vary in blade length in a second operating mode for optimal acoustic performance, and are retracted in a third operating mode for optimal forward flight performance.

It is yet another object of the present invention to provide a VDR system for reducing BVI noise which VDR system includes telescoping rotor blade assemblies and a positioning means for controlling the length of the rotor blade assemblies, which positioning means does not adversely impact the weight and/or mechanical complexity of the VDR system.

These and other objects are achieved by a rotor system having odd and even blade assemblies mounting to and rotating with a rotor hub assembly wherein the odd blade assemblies define a radial length R_(O), and the even blade assemblies define a radial length R_(E) and wherein the radial length R_(E) is between about 70% to about 95% of the radial length R_(O).

Other embodiments of the invention are directed to a Variable Diameter Rotor system which may be reconfigured in various operating modes for optimizing aerodynamic and acoustic performance. A Variable Diameter Rotor system in accordance with the present invention includes odd and even blade assemblies having inboard and outboard blade sections wherein the outboard blade sections telescopically mount to the inboard blade sections. A positioning means is provided for positioning the outboard blade sections with respect to the inboard blade sections such that the radial length R_(E) of the even blade assemblies is equal to the radial length R_(O) of the odd blade assemblies in a first operating mode, and such that the radial length R_(E) is between about 70% to about 95% of the length R_(O) in a second operating mode.

BRIEF DESCRIPTION OF THE DRAWINGS

A more complete understanding of the present invention and the attendant features and advantages thereof may be had by reference to the following detailed description of the invention when considered in conjunction with the following drawings wherein:

FIG. 1 is a top view of a rotor system in accordance with the present invention wherein odd and even rotor blade assemblies thereof alternately vary in length about the azimuth of the rotor system;

FIG. 2a depicts a two dimensional top view of the vortices shed by the rotor blade assemblies of a conventional rotor system;

FIG. 2b is a section view along a vertical plane 2b of FIG. 2a, depicting the interaction of vortices of the conventional rotor system, and the spatial positioning of the vortices over time due to such interaction;

FIG. 2c depicts a vortex of the conventional rotor system interacting with a blade element thereof;

FIG. 3a depicts a two dimensional top view of the vortices shed by the rotor blade assemblies of the rotor system according to the present invention;

FIG. 3b is a section view along a vertical plane 3b of FIG. 3a, depicting the interaction of vortices of the conventional rotor system, and the spatial positioning of the vortices over time due to such interaction;

FIG. 3c depicts vortices of the rotor system according to the present invention and a blade element thereof passing above or below the vortices;

FIG. 4a is a graphical representation of an acoustic pressure profile illustrating the magnitude of BVI noise radiated from the conventional rotor system;

FIG. 4b is a graphical representation of an acoustic pressure profile illustrating the magnitude of BVI noise radiated from the rotor system of the present invention;

FIG. 5a-5c depicts a tilt rotor aircraft in combination with a pair of Variable Diameter Rotor systems wherein the odd and even blade assemblies are extended in a first operating mode (FIG. 5a), alternately vary in blade length in a second operating mode (FIG. 5b) and are s retracted in a third operating mode (FIG. 5c);

FIG. 6a depicts a plan view of a telescoping blade assembly having inboard and outboard blade sections which are broken-away and sectioned to reveal an internal positioning means for varying blade length;

FIG. 6b is a cross-sectional view taken substantially along line 6b--6b of FIG. 6a;

FIG. 6c is an enlarged view of the root end portion of the blade assembly of FIG. 6a;

FIG. 6d is a cross-sectional view taken substantially along line 6d--6d of FIG. 6a;

FIGS. 7 depicts an enlarged view of the relevant portions of the positioning means including: a centrifugal restraint assembly disposed in combination with the outboard blade section and in combination with an internal stop surface, and an actuation means including a drive means and a ballscrew assembly operative for engaging and disengaging the centrifugal restraint assembly;

FIG. 8 is a partially broken-away side view of the drive means for effecting rotation of the ballscrew assembly;

FIG. 9 depicts the positioning means in two operating positions wherein a ball nut element of the ballscrew assembly is disengaged from the centrifugal restraint assembly in one operating mode such that the centrifugal restraint assembly engages the stop surface and wherein the ball nut is engaged with the centrifugal restraint assembly in another operating mode;

FIGS. 10a-10c schematically depict one embodiment of the positioning means in first, second and third operating modes wherein ballscrew assemblies are employed for effecting telescopic translation of the odd and even blade assemblies and wherein the relative position of the ball nuts effects the desired blade length variation;

FIGS. 11a-11c schematically depict another embodiment of the positioning means in the first, second and third operating mode wherein ballscrew assemblies are employed for effecting telescopic translation of the odd and even blade assemblies and wherein the relative position of the stop surfaces effects the desired blade length variation;

FIG. 12a depicts a broken-away top view of a telescoping rotor blade wherein the positioning means employs a reeling assembly having end fixities for engaging or disengaging the centrifugal restraint assembly;

FIG. 12b is a cross-sectional view taken substantially along line 12b--12b of FIG. 12a;

FIG. 12c is a cross-sectional view taken substantially along line 12c--12c of FIG. 12a;

FIG. 12d depicts a broken-away and partially sectioned side view of the reeling assembly in combination with an overhead planetary gear system for driving the reeling assembly;

FIG. 12e is an enlarged view of the overhead planetary gear system which is operative for driving a cylindrical drum of the reeling assembly;

FIG. 12f is a cross-sectional view taken substantially along lines 12f--12f of FIG. 12d;

FIGS. 13a-13c schematically depict another embodiment of the positioning means in first, second and third operating modes wherein the reeling assembly is employed for effecting telescopic translation of the odd and even blade assemblies and wherein the relative position of the end fixities effects the desired blade length variation;

FIGS. 14a-14c schematically depict yet another embodiment of the positioning means in the first, second and third operating mode wherein the reeling assembly is employed for effecting telescopic translation of the odd and even blade assemblies and wherein the relative position of the stop surfaces effects the desired blade length variation.

BEST MODE FOR CARRYING OUT THE INVENTION

The present invention is applicable to a variety of rotor systems, e.g., fixed and variable diameter rotors, but, for the purposes of the following discussion, the invention will be described in the context of a Variable Diameter Rotor (VDR) system. The present invention is particularly well-suited for application to VDR systems inasmuch as the mechanisms employed in such rotors may be readily adapted to maximally exploit the teachings and advantages of the invention.

Referring now to the drawings wherein like reference characters identify corresponding or similar elements throughout the several views, FIG. 1 depicts a plan view of a four-bladed VDR system 4 having a rotor hub assembly 6 mounting to and driving odd and even rotor blade assemblies O_(b) and E_(b), respectively, about an axis of rotation 8. While the described embodiment depicts a four-bladed VDR system 4, the invention is also applicable to rotor systems having an even number of rotor blade assemblies in excess of four, e.g., 6 or 8 rotor blade assemblies. The odd and even blade assemblies O_(b), E_(b) of the VDR system 4 each include inboard and outboard blade sections 10 and 12, respectively, wherein the outboard blade section 12 telescopically mounts to the inboard blade section 10. Furthermore, the telescoping rotor blade assemblies O_(b), E_(b) alternate in radial length about the azimuth of the rotational axis 8 such that the tip path of the odd and even rotor blade assemblies O_(b) and E_(b) define two distinct rotor diameters D_(O), and D_(E), respectively. The positioning means for alternating blade length are described in detail below, however, suffice it to say that the telescopic translation of the odd and even blade assemblies O_(b), E_(b) may be controlled to vary the radial length of each.

Each odd blade assembly O_(b), defines a radial length R_(O) which may be further defined as the fully-extended blade radius of the VDR system 4, i.e., the maximum permissible length of the telescoping inboard and outboard blade sections 10, 12. Each even blade assembly E_(b) defines a radial length R_(E) which may be further defined as a percentage of the radial length R_(O) of each odd blade assembly O_(b). Preferably, the radial length R_(E) is between a range of about 70% to about 95% of radial length R_(O) and, more preferably, the radial length R_(E) is between about 82% to about 95% of radial length R_(O). The functional significance of the selected ranges will become apparent in view of the following discussion.

In FIGS. 2a-2c and FIGS. 3a-3c, the BV Interactions of a conventional, uniform blade length rotor system 14 are compared and contrasted with those of the alternating blade length VDR system 4 of the present invention. In FIG. 2a, the rotor blades B₁ -B₄ of the conventional rotor system 14 produce vortices V₁ -V₄ which are plotted over a period of one revolution. As shown, the rotor system 14 is moving forward at a velocity V_(F) and in a descending flight profile. The two dimensional vortex plot shows a high concentration of vortices V₁ -V₄ in the first quadrant of the rotor system 14 i.e., between 0 and 90 degrees. In FIG. 2b, the vortices V₁ -V₄ are shown in section through a vertical plane 2b located in the second quadrant. Initially, the vortices V₁ -V₄ are above the plane XY of the rotor, and are moving downward at velocity V_(z). Furthermore, the vortices V₁ -V₄, are rotating in a clockwise direction and are substantially equally-spaced with respect to one another i.e., in both horizontal and vertical directions. As time advances, the vortices V₁ -V₄ interact such that they remain in substantially collinear alignment, i.e., along line L_(v), as the vortices V₁ -V₄ progress in a downward direction. That is, the alternating upward and downward circulation of the vortices V₁ -V₄ produce induced velocity vectors I_(v) which are substantially equal and opposite, thereby maintaining the vertical spacing between the vortices V₁ -V₄. Such uniform vertical spacing creates a high probability that a subsequent rotor blade will interact with one of the Vortices V₁ -V₄. FIG. 2c depicts a typical BV interaction in the first quadrant wherein the Vortex V₂ is in close proximity to a blade element B_(e) of rotor blade B₁ and is substantially parallel thereto. As discussed in the "Background of the Invention" such close proximity, parallel interactions result in high BVI noise.

In FIGS. 3a-3c, the odd and even rotor blade assemblies O_(b) and E_(b) of the VDR system 4 according to the present invention produce vortices V_(O) and V_(E), respectively. The same flight conditions and views are shown as those depicted in FIGS. 2a-2c, however, the trajectory and spatial separation of the vortices V_(O) and V_(E) are altered due to the variation of blade length. More specifically, and referring to FIG. 3b, the vortices V_(O), V_(E) are initially clustered in closely spaced pairs P₁ and P₂, wherein the pairs P₁, P₂ are distally spaced in a horizontal direction. As time advances, the vortices V_(O), V_(E) of each pair P₁, P₂ interact to effect an increased spatial separation in a vertical direction. That is, the horizontal separation of the vortex pairs P₁, P₂ causes the induced velocity vectors I_(v), to influence each pair P₁, P₂ independently, i.e., without influencing each other. The induced velocity I_(v) causes the vortices V_(O), V_(E) of each pair to separate vertically, i.e., by impeding the downward progression of vortices V_(E) while accelerating the downward motion of vortices V_(O). While it may have been expected that the vortices V_(O), V_(E) of each pair P₁, P₂ should rotate about one another without effecting a vertical separation, additional factors such as the proximity of each vortex pair P₁, P₂ to prior generated vortices and the curvature/orientation of the vortices V_(O), V_(E) combine the produce to phenomena described above. As shown in FIG. 3c, the spatial separation causes the blade element B_(e) to pass above or below the vortices V_(O), V_(E) by a distance R_(s), wherein R_(s) is at least 5X the thickness of the blade element. As discussed earlier, such spatial separation results in substantially benign BV Interactions.

FIGS. 4a and 4b graphically depict the acoustic pressure profiles of the conventional rotor system 14 and the VDR system 4 of the present invention. In FIG. 4a, the conventional rotor system 14 produces rapid pressure fluctuations 18 having min and max values from about -40 PA (-8.4 lb/ft²) to about +40 PA (+8.4 lb/ft²), respectively, over a 1-3 msec time interval. The pressure fluctuations 18 are indicative of high impulsive pressure waves which are the source of BVI noise. Secondary spikes 20 are indicative of pressure waves generated by blade loading, e.g., lift, and are less offensive to the human ear due to the longer time interval, i.e., 20-25 msec, over which such fluctuations occur. In FIG. 4b, the VDR system of the present invention produces substantially reduced BVI impulses 24 which fluctuate from about -10 PA (-2.2 lb/ft²) to +10 PA (+2.2 lb/ft²). Secondary spikes 26 and 28 are indicative of the blade loading on the even and odd blade assemblies O_(b) and E_(b), respectively, and fluctuate in magnitude due to the alternating blade length. When comparing the BVI components of pressure in FIGS. 4a and 4b, and converting the same to the frequency domain, a 10-16 dBa reduction in BVI noise is achieved when employing the teachings of the present invention.

The present invention is applicable to fixed or Variable Diameter Rotor systems. For fixed diameter rotor systems, an analysis and trade-study will be conducted to determine the optimum variation in blade length (within the above specified ranges) which result in acceptable aerodynamic and acoustic performance. Generally, the lower limit of the range will be determined by the required lift performance of the blade assembly and the upper limit of the range will be determined by the desired acoustic performance.

Improved aerodynamic and acoustic performance may be obtained through the use of VDR systems insofar as such rotor systems may be configured for optimum performance in various modes of flight operation. For example, all blade assemblies O_(b), E_(b) thereof may be fully-extended and uniform in length, in a first operating mode corresponding to hover or forward flight operations. In this configuration, the rotor disk area is maximized for optimum aerodynamic performance. Furthermore, the blade assemblies O_(b), E_(b) may be selectively positioned for alternating blade length in a second operating mode corresponding to descending flight operations. In this configuration, BVI noise is mitigated for maximum acoustic performance. Moreover, VDR systems permit substantially greater design flexibility, insofar as the optimum blade length variation may be achieved through minor modifications of the rotor blade assemblies and/or the rotor system.

Application to Tilt Rotor Aircraft

While the present invention is useful in combination with VDR systems in general, its application to tilt rotor aircraft provides a considerable opportunity for BVI noise reduction. A tilt rotor aircraft is a type of rotorcraft which employs a pair of rotor systems which are supported at the outermost end of a wing structure and are pivotable such that the rotors thereof may assume a vertical or horizontal orientation. In a horizontal orientation, the aircraft is capable of hovering flight, while in a vertical orientation, the aircraft is propelled in the same manner as conventional propeller-driven fixed-wing aircraft.

Currently, tilt rotor aircraft employ conventional fixed-diameter rotor systems which, in the aerodynamic, acoustic and aeroelastic design thereof, attempt to blend the competing requirements of hovering and forward flight modes of operation. For example, with regard to hovering flight, it is generally advantageous to employ a large diameter rotor to improve hovering performance by lowering disk loading, reducing BVI noise levels, and reducing downwash velocities. Conversely, a relatively small diameter rotor is desirable in forward flight to improve propulsive efficiency by minimizing blade aeroelastic properties, minimizing blade area, and reducing tip speed (Mach number). Within the constraints of a fixed-diameter rotor system, these requirements necessitate that design compromises be made which result in non-optimum aerodynamic and acoustic performance. With regard to acoustic performance, high blade loading in descending flight modes produces highly vexatious BVI noise.

Variable Diameter Rotor (VDR) systems are known to provide distinct advantages over conventional fixed-diameter rotors insofar as such systems are capable of adaptation to both modes of operation. That is, when the plane of the rotor is oriented horizontally, the rotor diameter is enlarged for improved hovering efficiency and, when oriented vertically, the rotor diameter is reduced for improved propulsive efficiency. Tilt rotor aircraft which employ VDR systems are described and depicted in U.S. Pat. Nos. 3,768,923, 4,142,697, and 5,253,979. VDR systems for use in combination with tilt rotor aircraft provide a reduction in blade loading and, consequently, a degree of BVI noise reduction. Further improvements, however, are achievable when employing the teachings of the present invention.

The subsequent discussion will address various positioning means for varying the length of VDR blade assemblies. The mechanisms are useful for any variety of VDR system, but are described in the context of a tilt rotor aircraft wherein all the blade assemblies may be extended, alternately varied in length, or retracted. More specifically, and referring to FIGS. 5a-5c, the blade assemblies O_(b), E_(b) of the VDR systems 4 are extended in a first operating mode corresponding to hover or low speed flight operations (FIG. 5a), are alternately varied in blade length in a second operating mode corresponding to descending flight operations (FIG. 5b), and are retracted in a third operating mode corresponding to high speed cruise flight operations (FIG. 5c).

Ballscrew Arrangement for Varying Blade Length

Inasmuch as the telescoping features and blade positioning means are similar for all blade assemblies O_(b), E_(b), it will facilitate the discussion to describe one of the blade assemblies, e.g., the odd blade assembly O_(b), with the objective of describing those features which are common to both odd and even blade assembles O_(b), E_(b). Subsequently, the discussion will distinguish between the odd and even rotor blade assemblies O_(b) and E_(b), to identify structural and functional differences therebetween which facilitate control of rotor blade length.

In FIG. 6a, the odd blade assembly O_(b) is broken away to reveal the internal arrangement for varying blade length. The outboard blade section 12 telescopically mounts to the inboard blade section 10 (hereinafter referred to as a torque tube member). More specifically, the outboard blade section 12 includes a spar member 34 which is enveloped by a leading edge sheath 36 (FIG. 6b) and a foam-filled trailing edge pocket assembly 38 to define the requisite aerodynamic contour of the outboard blade section 12. The spar member 34 is coaxially aligned with and accepts the torque tube member 10 so as to permit telescopic translation thereof relative to the torque tube member 10.

Coaxial alignment of the torque tube and spar members 10, 34 may be effected by any conventional bearing assembly such as a rolling element bearing assembly, however, in the described embodiment, the s bearing assembly includes a first bearing block 40a mounted to the outboard end of the torque tube member 10 and a second bearing block 40b mounted to the inboard end of the spar member 34, and preferably internally thereto. The first bearing block 40a slideably engages an internal pilot surface 42 formed within the spar member 34 and the second bearing block 40b slideably engages an external pilot surface 44 formed about the exterior of the torque tube member 10.

In FIG. 6c, the root end of the torque tube member 10 is adapted for mounting to a cuff assembly 50 which is journally mounted to a radial arm 52 of the rotor hub assembly 6. The cuff assembly 50 engages a flared root end portion 54 of the torque tube member 10 by means of a correspondingly shaped internal restraint member 56 and an external restraint sleeve 58. The cuff assembly 50, furthermore, includes a pitch control arm 60 through which pitch control inputs are made about the feathering axis 62 of the blade assembly O_(b).

In FIG. 7, the torque tube and spar members 10, 34 define an internal chamber 64 for accepting a blade positioning means 70. The positioning means 70 is operative to position the outboard blade section 12 relative to the torque tube member 10 and, consequently, vary the radial length of the blade assembly O_(b). The positioning means 70 includes: a centrifugal restraint assembly 80, a stop surface 64s formed internally of the chamber 64, and an actuation means 90 operative for engaging and disengaging the centrifugal restraint assembly 80.

The centrifugal restraint assembly 80 includes a retention block 82, a cradle member 84 and a connecting means 86 disposed between and mechanically coupling the retention block 82 to the cradle member 84. The retention block 82 is disposed in combination with the outboard blade section 12 and is operative, in combination with the connecting means 86, for transferring centrifugal loads C_(f) acting on the outboard blade section 12 to the cradle member 84. A retention block of the type described is fully disclosed in co-pending, commonly owned U.S. patent application Ser. No. 08/412,035 (therein referred to as a "restraint assembly"). Preferably, the connecting means 86 for coupling the retention block 82 to the cradle member 84 includes fore and aft cable members 86a and 86b, respectively, which are compliant for accommodating various motions of the rotor blade assembly O_(b).

The cradle member 84 is a generally U-Shaped member having radially extending arms 84a and a base portion 84b for structurally interconnecting the inboard ends of the radial arms 84a. The radial arms 84a are mechanically coupled to the connecting means 86 and are disposed in sliding combination with an internal wall 64w of the chamber 64 for permitting radial translation of the cradle member 84 therein.

The actuation means 90 includes a ballscrew assembly 92 disposed within the internal chamber 64, and a drive means 100 disposed internally of the rotor hub assembly 6. More specifically, the ballscrew assembly 92 includes a threaded ballscrew 94 which extends through an aperture 84h (FIG. 6b) formed in the base portion 84b of the cradle member 84 and is operative for rotation in a clockwise or counterclockwise direction about its longitudinal axis 94L. The ballscrew 94 is supported at an inboard end by a first journal bearing 96a (FIG. 6c) and, at an outboard end, to a second journal bearing 96b (FIG. 6a) disposed in combination with the outboard end of the torque tube member 10. The actuation means 90 further includes a ball nut 98 which is disposed in combination with the threads of the ballscrew 94, and positioned radially outboard of the cradle member 84. Furthermore, the ball nut 98 is operative, in response to rotation of the ballscrew 94, to translate axially along the longitudinal axis 94L thereof. Rotational restraint of the ball nut 98 is provided by the internal geometry of the torque tube member 10 (FIG. 6d). Ballscrew assemblies of the type described are available from Thomson Saginaw, located in Saginaw, Mich.

The drive means 100 effects rotation of the ballscrew 94 and, consequently, axial displacement of the ball nut 98. In FIG. 8, the drive means 100 includes an input shaft 102 disposed internally of and coaxial with the main rotor shaft 104 which supports and drives the rotor assembly 6 about its rotational axis 8. The input shaft 102 drives an input bevel gear 106i through a first universal joint 108-1 which accommodates gimbal tilt motion of the rotor hub assembly 6. The input bevel gear 106i drives an output bevel gear 106o, one per blade assembly, which is coupled, via a second universal joint 108-2 to the ballscrew 94. The ballscrew 94 may be driven in either direction or, alternatively, rotationally fixed by controlling the rotational speed of the input shaft 102 relative to the main rotor shaft 104. For example, by driving the input shaft 102 and, consequently, the input bevel gear 106i, at a higher rotation speed than the main rotor shaft, the output bevel gear 106o, which is rotating with the main rotor shaft 104, will be driven in the direction of the speed differential. If the input drive shaft 102 rotates at the same operational speed as the main rotor shaft 104, no differential rotation is effected between the input and output bevel gears 106i, 106o, hence the ballscrew 94 will remain rotationally fixed. Drive means which are structurally and functionally similar to that described above are discussed in U.S. Pat. Nos. 4,142,697, 4,009,997, 3,884,594 and 3,713,751.

In FIG. 9, the cradle member 84 is outwardly biased by centrifugal forces C_(f) acting on the outboard blade section 12 such that the cradle member 84 is disposed in abutting engagement with the ball nut 98 or the stop surface 64s to determine the radial length of the rotor blade assembly O_(b). In one of the operating modes, the cradle member 84 engages the stop surface 64s vis-a-vis a first bearing surface 84s-1 thereof such that the rotor blade assembly O_(b) is fully-extended, i.e., at its maximum permissible length. Centrifugal loads C_(f) acting on the outboard blade section are transferred to the cradle member 84 and reacted by the stop surface 64s. In another operating mode, the ball nut 98 is transpositioned, in response to rotation of the ballscrew 94, so as to engage the cradle member 84 vis-a-vis a second bearing surface 84s-2 thereof. In this operating mode, the cradle member 84 follows the ball nut 98 provided, however, that the first bearing surface 84s-1 is disengaged from the stop surface 64s. Furthermore, centrifugal loads acting on the outboard blade section 12 are transferred to the actuation means 90 via the cradle member 84. The outboard blade section 12 is thereby caused to telescope inwardly or outwardly depending upon the directional displacement of the ball nut 98.

The foregoing discussion has described the structural elements which are common to all blade assemblies O_(b), E_(b) of the VDR system 4. The following discussion addresses the structural or functional differences between odd and even blade assemblies O_(b), E_(b) which produce the desired blade length variations. A subscript "O" or "E" will be used to distinguish between odd to even blade assemblies, O_(b) to E_(b).

In FIGS. 10a-10c, one embodiment of the present invention is shown wherein the positioning means 70 for controlling blade length is schematically depicted. Each schematic depicts the first, second, and third operating modes corresponding to FIGS. 5a, 5b and 5c, respectively. Representative odd and even blade assemblies O_(b), E_(b) are arranged in side-by-side relation for ease of comparison. Moreover, the external structures which envelop the positioning means 70, e.g., the spar member 34, torque tube member 10, rotor hub assembly 6 etc., have been removed to facilitate the discussion.

While many elements of the positioning means 70 have been previously described in the context of the odd blade assembly O_(b), it should be understood that the positioning means 70 controls the blade length of all blade assemblies, i.e., odd and even blade assemblies O_(b), E_(b). In FIG. 10a, the ballscrews 94_(O), 94_(E) are supported between the first and second bearing assemblies and extend through the respective cradle members 84_(O), 84_(E) such that the ball nuts 98_(O), 98_(E) are disposed radially outboard thereof. Furthermore, the ball nuts 98_(O) and 98_(E) are positioned along the respective ballscrews 94_(O) and 94_(E) so as to define radial distances Rn_(O) and Rn_(E), respectively, measured from the rotational axis 8 of the rotor hub assembly. Initially, the relative position of the ball nuts 98_(O), 98_(E) is prescribed such that the ball nut 98_(E) of the even blade assembly E_(b) is radially inboard of the ball nut 98_(O) of the odd blade assembly O_(b). The functional significance of such relative position will become apparent in the subsequent views.

In the first operating mode, the ballnuts 98_(O), 98_(E) are disengaged from the cradle members 84_(O), 84_(E) such that the cradle members 84_(O), 84_(E), in response to centrifugal loads C_(f), are disposed in abutting engagement with the stop surfaces 64s_(O), 64s_(E). Insofar as the length of the centrifugal restraint assemblies 80_(O), 80_(E) is preferably constant i.e., from odd to even blade assemblies O_(b), E_(b), the radial distances Rs_(o), Rs_(E) defined by the stop surfaces 64s_(O), 64s_(E) determine the maximum permissible length R_(O), R_(E) of the odd and even rotor blade assemblies O_(b), E_(b). In the described embodiment, the radial distance Rs_(O) of the odd blade assembly O_(b) is equal to the radial distance Rs_(E) of the even blade assembly E_(b), such that blade assemblies O_(b), E_(b) are fully-extended and equal in radial length. Such blade assembly configuration provides maximum rotor disk area for optimum aerodynamic performance.

In the second operating mode (FIG. 10b), the ball nuts 98_(O) and 98_(E) are transpositioned inwardly to an intermediate position in response to rotation of the respective ballscrews 94_(O), 94_(E) by the drive means 100. Inasmuch as the ball nut 98_(E) is disposed radially inboard of the ball nut 98_(O), the ball nut 98_(E) engages the respective cradle member 84_(E) thereby effecting inward telescopic translation of the outboard blade section 12_(E). The ball nut 98_(O) of the odd blade assembly O_(b) also translates inwardly, but does not engage the respective cradle member 84_(O). When disposed in their respective intermediate positions, the ball nut 98_(E) is disposed in abutting engagement with the respective cradle member 84_(E) and the ball nut 98_(O) is disengaged from the respective cradle member 84_(O). Consequently, the cradle member 84_(O) remains in abutting engagement with the stop surface 64s_(O).

In view of the foregoing, it will be appreciated that the radial distances Rn_(O), Rn_(E) defined by the ball nuts 98_(O), 98_(E) determines the maximum permissible variation in blade assembly length R_(O), R_(E). That is, by suitably positioning the ball nuts 98_(O), 98_(E) along the respective ballscrews 94_(O), 94_(E), the length R_(E) of the even blade assembly E_(b) may be altered without influencing the radial length R_(O) of the odd blade assembly O_(b). More specifically, the ball nuts 98_(O), 98_(E) are positioned such that radial distance Rn_(E) of ball nut 98_(E) is between about 0.7Rn_(O) -0.3L to about 0.95Rn_(O) -0.05L, and, preferably, between about 0.83Rn_(O) -0.17L to about 0.92Rn_(O) -0.08L, wherein L is the length from one of the cradle members 84_(O), 84_(E) to the tip end of the one of the outboard blade section 12_(O), 12E. This is also based on the assumption that the lengths L from odd to even blade assemblies O_(b), E_(b) are equal. Consequently, the odd and even blade assemblies O_(b), E_(b), may be varied in length by an amount proportional to the radial spacing of the ball nuts 98_(O), 98_(E). This blade assembly configuration is effected in a descending flight mode for optimum acoustic performance, i.e., BVI noise reduction.

In the third operating mode (FIG. 10c), the ball nuts 98_(O) and 98_(E), and consequently, the cradle members 84_(O), 84_(E), are transpositioned inwardly to a fully-inboard position. During the transition, the ball nut 98_(O) of the odd blade assembly O_(b) engages the respective cradle member 84_(O) and translates inwardly at an increased linear rate relative to the ball nut 98_(E). The linear rate differential causes the ball nuts 98_(O) and 98_(E) to reach their respective inboard positions at the same time, i.e., such that the radial distance Rn_(E) equals the radial distance Rn_(O). Such rate differential may be effected by varying the thread pitch of the ballscrews 94_(O), 94_(E), varying the rotational speed of the ballscrews 94_(O), 94_(E), or a combination thereof. With regard to the former, a thread pitch differential may be effected by increasing the thread pitch of the ballscrews 94_(O) with respect to the thread pitch of the ballscrews 94_(E). The pitch differential causes the ball nuts 98_(O), 98_(E) to traverse at different linear rates such that at an inboard radial position, the radial distances Rn_(O), Rn_(E) of the ball nuts 98_(O), 98_(E) are equal. With regard to the latter, a speed differential may be effected by altering the gear ratios of the input and output bevel gears 106i, 106o_(O), 106o_(E) such that the rotational speed of ballscrew 94_(O) is greater than the rotational speed of ballscrew 94_(E).

When in their respective inboard positions, the ball nuts 98_(O), 98_(E) are disposed in abutting engagement with the cradle members 84_(O), 84_(E) and the blade assemblies O_(b), E_(b) are fully-retracted. Such blade assembly configuration corresponds to high speed cruise flight operations wherein the rotor disk is vertically oriented for maximum propulsive efficiency.

Another embodiment of the positioning means 70 is shown in FIGS. 11a -11c wherein the same operating modes are depicted as those illustrated and described in FIGS. 10a-10c. In this embodiment of the invention, the radial distances Rn_(O), Rn_(E) defined by the ball nuts 98_(O), 98_(E) are equal, and the radial distances Rs_(O), Rs_(E) defined by the stop surfaces 64s_(O), 64s_(E) determine the percentage variation in blade length R_(O), R_(E). In the first operating mode, (FIG. 11a) ballnut 98_(O) of the odd blade assembly O_(b) is disposed in abutting engagement with the cradle member 84_(O) and the ball nut 98_(E) of the even blade assembly E_(b) is disengaged from the cradle member 84_(E) thus causing the cradle member 84_(E) to be disposed in abutting engagement with the stop surface 64s_(E). The radial distances Rn_(o) and Rs_(E) defined by the ball nut 84_(O) and the stop surface 64s_(E), respectively, are substantially equal such that the odd and even blade assemblies O_(b), E_(b) are extended, and the radial length R_(O) of the even blade assembly O_(b) is equal to the radial length R_(E) of the even blade assemblies E_(b). These radial distances Rn_(O), Rs_(E) may vary depending upon the configuration of the cradle member 84_(O), 84_(E).

In the second operating mode, (FIG. 11b) the ball nuts 98_(O), 98_(E) are transpositioned to an outboard position such that the cradle member 84_(O) of the odd blade assembly O_(b) also engages the respective stop surface 64s_(O). Consequently, the odd blade assembly O_(b) will translate radially outboard to its fully-extended position while the even blade assembly E_(b) remains fixed due to the axial restraint provided by the stop surface 64s_(E). In this embodiment of the invention, the maximum permissible variation in blade assembly length R_(O) and R_(E) is effected by varying the radial distances Rs_(O), Rs_(E) of the stop surfaces 64s_(O), 64s_(E). More specifically, the stop surfaces 64s_(O), 64s_(E) are positioned such that the radial distance Rs_(E) is between about 0.7Rs_(O) -0.3L to about 0.95Rs_(O) -0.05L, and, preferably, between about 0.83Rs_(O) -0.17L to about 0.95Rs_(O) -0.08L wherein L is the length from one of the cradle members 84_(O), 84_(E) to the tip end of the one of the outboard blade section 12O, 12E. Again, it is assumed that the length L is equal from odd to even blade assemblies O_(b), E_(b). Consequently, the odd and even blade assemblies O_(b), E_(b) may be varied in length by an amount proportional to the radial spacing of the stop surfaces 64s_(O), 64s_(E).

In the third operating mode (FIG. 11c), the ball nuts 98_(O), 98_(E) engage the cradle members 84_(O), 84_(E) and translate to a fully inboard position. During the transition from the second to third operating modes, the ball nut 98_(O) of the odd blade assembly O_(b) initially engages the respective cradle member 84_(O) and, subsequently, the ball nut 98_(E) of the even blade assembly engages its respective cradle member 84_(E). With both cradle members 84_(O), 84_(E) engaged, the outboard blade sections 12_(O), 12_(E) telescope inwardly, in unison, to the desired fully-inboard position. When in their respective inboard positions, the ball nuts 98_(O), 98_(E) are disposed in abutting engagement with the cradle members 84_(O), 84_(E) and the blade assemblies O_(b), E_(b) are fully-retracted.

While the described embodiment employs an actuation means 70 having a ballscrew assembly 92 for effecting telescopic translation of the blade assemblies O_(b), E_(b), it will be appreciated that other devices such as a threaded jackscrew/nut or a threaded rollerscrew/roller nut may be substituted therefor. Furthermore, while the described embodiment employs a cradle member 84 having a generally U-shape, it will be appreciated that the configuration of the cradle member may take any form. For example, a simple cross member which conforms to the shape of the internal chamber 64 may functionally replace the U-shaped cradle member 84. While the described embodiment includes cable members 86a, 86b for connecting the retention block 82 to the cradle members 84, it will be appreciated that other means are contemplated. For example, strap or compliant tubular members which are capable of withstanding high tensile loads may be employed in lieu of the cable members 86a, 86b.

Reeling Assembly for Varying Blade length

Other embodiments of the positioning means 70 are shown in FIGS. 12a-12f, 13a-13c, and 14a-14c wherein the actuation means 90 includes a reeling assembly 110 and means 120 for driving the reeling assembly 110. Again, it will facilitate the discussion to describe the positioning means 70 with respect to one blade assembly and subsequently discuss the features thereof which permit independent control of odd and even blade assemblies for varying blade length.

In FIGS. 12a-12c, the reeling assembly 110 includes a cylindrical drum 112 operative for rotation about the rotor hub assembly axis 8, an end fixity 114 disposed internally of the chamber 64 and operative for engaging and disengaging the cradle member 84, and strap means 116 for connecting the end fixity 114 to the cylindrical drum 112. More specifically, the end fixity 114 is disposed radially outboard of the cradle member 84 and disposed in sliding combination with the connecting means 86 (FIG. 12b) and/or an internal wall 64ws of the chamber. The strap means 116 is mechanically coupled to the end fixity 114 and extends through the aperture 84h of the cradle member 84 (FIG. 12c) for connecting to the cylindrical drum 112. Depending upon the rotational sense of the cylindrical drum 112, the strap means 116 is wound-up or let-out such that the end fixity 114 is operative to engage the cradle member 84 or, alternatively, disengage from the cradle member 84 such that the cradle member engages the stop surface 64s. When the end fixity 114 is engaged with the cradle member 84, centrifugal loads C_(f) acting on the outboard blade section 12 are transferred to the cylindrical drum 112.

In FIG. 12d-12f, the cylindrical drum 112 is disposed internally of the rotor hub assembly 6 and may be driven in either direction by the drive means 120. The drive means 120 includes an overhead planetary gear system 140 which is driven by an input drive shaft 122. More specifically, the input drive shaft 122 includes: an upper stub shaft portion 122u which is supported by an upper mounting fixture 126 of the rotor hub assembly 6 via a bearing assembly 128, a lower drive shaft portion 122L coaxially aligned with the main rotor shaft 104, and a universal joint 130 disposed therebetween for accommodating gimbal tilt motion of the rotor hub assembly 6. The cylindrical drum 112 is supported for rotation about the stub shaft portion 122u via a bearing assembly 132, thereby permitting the drum 112 to synchronously tilt with the rotor hub assembly 6.

The planetary gear system 140 includes: a driving sun gear 142 coaxially aligned with the rotor hub assembly axis 8, a ring gear 144 rigidly affixed to the mounting fixture 126 of the rotor hub assembly 6, and a plurality of planetary pinions 146 disposed between and interacting with the sun and ring gears 142, 144. The sun gear 142 is spline connected to and driven by the stub shaft portion 122u of the input drive shaft 122 and drives the planetary pinions 146 about the rotor hub assembly axis 8. More specifically, the planetary pinions 146 traverse in an epicycle about the sun gear 142 at reduced rotational speed relative thereto due to interaction of the planetary pinion 146 with the ring gear 144. The output of the planetary pinions 146 is transferred to the cylindrical drum 112 by means of carrier posts 148 which are disposed in combination with each planetary pinion 146 and the upper surface 150 of the cylindrical drum 112.

It will be appreciated that the sum of the centrifugal loads C_(f) acting on the outboard blade sections 12 is reacted in torsion by the input drive shaft 122. By interposing the planetary gear system 140 in the load path, i.e., from the outboard blade section 12 to the input drive shaft 122, the torsional load imposed on the input drive shaft 122 is substantially reduced. That is, the planetary gear system 140, provides a mechanical advantage which substantially reduces the tangential loading on the sun gear 142, and, accordingly, the torsional loads on the input drive shaft 122. Consequently, the requisite size and/or thickness of the input drive shaft 122 may be reduced. In the described embodiment, the pitch diameter ratio Rs/Rp between the sun and planetary gears 142, 146 is about 0.75 and the face width, i.e., the height dimension, of the meshing teeth is about 7.5 in (19 cm). This combination of parameters reduces the torsional loading in the input drive shaft 122 by a factor of 4.

In FIGS. 13a-13c, an embodiment of the positioning means 70/reeling assembly 110 is schematically depicted, which embodiment is operationally similar to FIGS. 10a-10c. Similar to the earlier described embodiments, a subscript "O" and "E" will be used to differentiate between odd and even blade assemblies O_(b), E_(b).

In FIG. 13a, the cylindrical drum 112 of the reeling assembly 110 includes first and second cylindrical surfaces 112-1 and 112-2, respectively, which are disposed in biplanar relation. The first and second cylindrical surfaces 112-1 and 112-2 define diameter dimensions Dc1 and Dc2, respectively, wherein the diameter Dc1 of the first cylinder 112-1 is greater than the diameter Dc2 of the second cylinder 112-2. Furthermore, the strap means 116O and 116_(E) of the odd and even blade assemblies O_(b) and E_(b), respectively, are disposed in winding combination with the first and second cylinders 112-1 and 112-2, respectively. The length of the strap means 116O, 116_(E), is prescribed such that the end fixities 114_(O), and 114_(E) define radial distances Rf_(O), and Rf_(E), respectively, from the rotational axis 8 of the rotor hub assembly. Initially, the radial distance Rf_(O) is greater than radial distance Rf_(E).

In the first operating mode, the end fixities 114_(O), 114_(E) are disengaged from the cradle members 84_(O), 84_(E), such that the cradle members 84_(O), 84_(E) are disposed in abutting engagement with the stop surfaces 64s_(O), 64s_(E). In the described embodiment, the radial distances Rs_(O), Rs_(R) defined by the stop surfaces 64s_(O), 64s_(E) are equal, hence the blade assemblies O_(b), E_(b) are equal in radial length and are fully extended.

In the second operating mode (FIG. 13b), the end fixities 114_(O), 114_(E) are transpositioned inwardly to an intermediate position by rotation of the cylindrical drum 112 and wind-up of the respectively strap means 116O, 116_(E). During the transition, the end fixity 114_(E) of the even blade assembly E_(b) engages the respective cradle member 84_(E) thereby effecting inward telescopic translation of the outboard blade section 12_(E). The end fixity 114_(O) of the outboard blade section O_(b) also translates inwardly, but does not engage the respective cradle member 84_(O). When disposed in their respective intermediate positions, the end fixity 114_(E) is disposed in abutting engagement with the respective cradle member 84_(E) and the end fixity 114_(O) is disengaged from the respective the cradle member 84_(O) such that the cradle member 84_(O) remains in abutting engagement with the stop surface 64s_(O). Furthermore, the end fixities 114_(O), 114_(E) are positioned such that the radial distance Rf_(E) of the end fixity 114_(E) is between about 0.7Rf_(O) -0.3L to about 0.95Rf_(O) -0.05L and, preferably, between about 0.83Rf_(O) -0.17L to about 0.92Rf_(O) -0.08L, wherein L is the length from one of the cradle members 84_(O), 84_(E) to the tip end of the one of the outboard blade section 12_(O), 12_(E). Such relative position of the end fixities 114_(O), 114_(E) effects the s maximum permissible variation in blade length R_(O), R_(E).

In the third operating mode, (FIG. 13c), the end fixities 114_(O), 114_(E) engage the cradle members 84_(O), 84_(E) and are transpositioned inwardly to a fully inboard position. Insofar as the diameter Dc1 of the first cylindrical surface 112-1 is greater than the diameter Dc2 of the second cylindrical surface, the end fixity 114_(O) of the odd blade assembly O_(b) will translate inwardly at an increased linear rate relative to the end fixity 114_(E). The linear rate differential causes the end fixities 114_(O), 114_(E) to reach their respective inboard positions at the same instant in time, i.e., such that the radial distance Rf_(O) is equal to the radial distance Rf_(E).

In FIGS. 14a-14c, another embodiment of the positioning means 70/reeling assembly 110 is schematically depicted, which embodiment is operationally similar to FIGS. 11a-11c. In FIG. 14a, the cylindrical drum 112 defines a cylindrical surface 112s upon which the strap means 116_(O), 116_(E) may be wound on or off. The strap means 116_(O), 116_(E) are of equal length, and, consequently, the end fixities 114_(O), 114_(E) are equidistant from the rotational axis 8. Furthermore, the stop surfaces 64s_(O) and 64s_(E) define radial distances Rs_(O) and Rs_(E), respectively, wherein the radial distance Rs_(E) is between about 0.7Rs_(O) -0.3L to about 0.95Rs_(O) -0.05L and, preferably, between about 0.83Rs_(O) -0.17L to about 0.95Rs_(O) -0.08L wherein L is the length from one of the cradle members 84_(O), 84_(E) to the tip end of the one of the outboard blade section 12_(O), 12_(E).

In the first operating mode, the end fixity 114_(O) of the odd blade assembly O_(b) is disposed in abutting engagement with the cradle member 84_(O) and the end fixity 114_(E) of the even blade assembly E_(b) is disengaged from the cradle member 84_(E). Consequently, the cradle member 84_(E) is disposed in abutting engagement with the stop surfaces 64s. The radial distances Rf_(O) and Rs_(E) defined by the end fixity 114_(o) and the stop surface 64s_(E), respectively, are substantially equal such that the odd and even blade assemblies O_(b), E_(b) are extended, and the radial length R_(O) of the even blade assembly O_(b) is equal to the radial length R_(E) of the even blade assemblies E_(b).

In the second mode, (FIG. 14b), the end fixities 114_(O), 114_(E) are transpositioned to an outboard position, in response to rotation of the cylindrical drum 112, such that the cradle member 84_(O) of the odd blade assembly O_(b) also engages the respective stop surface 64s_(O). Consequently, the odd blade assembly O_(b) will translate to its fully-extended position while the even blade assembly E_(b) remains fixed due to the axial restraint provided by the stop surface 64s_(E). In this embodiment of the invention, maximum permissible variations in blade assembly length R_(O) and R_(E) may be effected by varying the radial distances Rs_(O), Rs_(E) of the stop surfaces 64s_(O) and 64s_(E), respectively.

In FIG. 14c, the end fixities 114_(O), 114_(E) engage the cradle members 84_(O), 84_(E) and translate to a fully inboard position. Insofar as the end fixities 114_(O), 114_(E) are equidistant from the rotational axis 8, the end fixity 114_(O) of the odd blade assembly O_(b) initially engages the respective cradle member 84_(O) and, subsequently, the end fixity 114_(E) of the even blade assembly engages its respective cradle member 84_(E). With both cradle members 84_(O), 84_(E) engaged, the outboard blade sections 12_(O), 12_(E) telescope inwardly, synchronously, to the desired inboard position. When in their respective inboard positions, the end fixities 114_(O), 144_(E) are disposed in abutting engagement with the cradle members 84_(O), 84_(E) and the blade assemblies O_(b), E_(b) are fully retracted.

The various embodiments of the positioning means 70 have minimal impact on the weight and/or mechanical complexity of the telescoping blade assemblies O_(b), E_(b). That is, the introduction of stop surfaces 64s_(O), 64s_(E) and cradle members 84_(O), 84_(E) have negligible impact on the overall weight of the rotor blade assemblies O_(b), E_(b). Furthermore, relatively minor modifications are required to effect a change in the rotor system configuration, i.e., in the second operating mode. For example, with respect to the embodiments depicted in FIGS. 10a-10c and 13a-13c, the initial radial position of the ball nuts 98_(O), 98_(E), or the length of the strap means 116_(O), 116_(E) may be changed to modify the maximum permissible blade length variation from odd to even blade assemblies O_(b), E_(b). With respect to the other described embodiments, the radial distances Rs_(O), Rs_(E) of the stop surfaces 64s_(O), 64s_(E) may be altered to effect the same result.

Furthermore, the pilot may control blade length, so as to selectively command blade length variations which are less than the maximum permissible blade length variation. For example, with respect to the embodiments depicted in FIGS. 10a-10c and 13a-13c, the ball nuts 98_(E) or end fixities 114_(E), may be positioned relative to the stop surfaces 64s_(O) so as to effect any combination of blade length variation within the prescribed ranges. With respect to the other embodiments the ball nuts 98_(O) or end fixities 114_(O) may be similarly positioned to effect the same result.

Although the invention has been shown and described with respect to exemplary embodiments thereof, it should be understood by those skilled in the art that the foregoing and other changes, omissions and additions may be made therein and thereto, without departing from the spirit and scope of the present invention. 

What is claimed is:
 1. A rotor system (4) for reducing Blade-Vortex Interaction (BVI) noise, comprising:a rotor hub assembly (6) defining an axis of rotation (8) about which said rotor hub assembly (6) rotates; and odd and even blade assemblies (O_(b), E_(b)) mounting to and rotating with said rotor hub assembly (6), said odd blade assemblies (O_(b)) defining a radial length R_(O), and said even blade assemblies (E_(b)) defining a radial length R_(E), said radial lengths R_(O) and R_(E) being measured from said axis or rotation (8); said radial length R_(E) being between about 82% to about 95% of said radial length R_(O).
 2. A Variable Diameter Rotor system (4) for rotorcraft and operative to reduce Blade-Vortex Interaction (BVI) noise, said rotorcraft operating in first and second operating modes, comprising:a rotor hub assembly (6) defining an axis of rotation (8) about which said rotor hub assembly (6) rotates; odd and even blade assemblies (O_(b), E_(b)) mounting to and rotating with said rotor hub assembly (6), each of said rotor blade assemblies (O_(b), E_(b)) having inboard and outboard blade sections (10, 12), said outboard blade section (12) telescopically mounted to said inboard blade section (10); said odd and even rotor blade assemblies (O_(b), E_(b)) each defining a radial length R_(O) and R_(E), respectively; and means (70) for positioning said outboard blade sections (12) with respect to said inboard blade sections (10) such that said radial length R_(E) of said even blade assemblies (E_(b)) is equal to said radial length R_(O) of said odd blade assemblies (O_(b)) in the first operating mode, and such that said radial length R_(E) is between about 70% to about 95% of said radial length R_(O) in the second operating mode.
 3. The Variable Diameter Rotor system (4) according to claim 2 wherein said positioning means (70) positions said outboard blade sections (12) with respect to said inboard blade sections (10) such that said radial length R_(E) is between about 82% to about 95% of said radial length R_(O) in the second operating mode.
 4. The Variable Diameter Rotor system (4) according to claim 2 wherein the second operating mode is a descending flight mode. 